CN1834490A - Fixed constant velocity universal joint - Google Patents

Fixed constant velocity universal joint Download PDF

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Publication number
CN1834490A
CN1834490A CNA2006100681978A CN200610068197A CN1834490A CN 1834490 A CN1834490 A CN 1834490A CN A2006100681978 A CNA2006100681978 A CN A2006100681978A CN 200610068197 A CN200610068197 A CN 200610068197A CN 1834490 A CN1834490 A CN 1834490A
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China
Prior art keywords
retainer
ball
ball groove
center
constant velocity
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Granted
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CNA2006100681978A
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CN1834490B (en
Inventor
铃木正
村山大
小林正纯
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NTN Corp
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NTN Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/2237—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
    • F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22303—Details of ball cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22309—Details of grooves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/10—Surface characteristics; Details related to material surfaces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
    • Y10S464/902—Particular material
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
    • Y10S464/904—Homokinetic coupling
    • Y10S464/906—Torque transmitted via radially spaced balls

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

A fixed constant velocity universal joint using eight torque transmitting balls has a ratio which a non-hardened layer assumes in a bar of a cage is set to be 0.30 C/S 0.75, which S represents a cross-sectional area of the bar and C represents an area of the non-hardened layer.

Description

Fixed constant velocity universal joint
Technical field
The present invention relates to a kind of fixed constant velocity universal joint that is used for automobile and various industrial machines, in particular to the fixed constant velocity universal joint that uses eight balls as the moment of torsion transfer member.
Background technique
Constant velocity universal joint (constant velocity universal joints) is divided into the permanent joint that can not slide and can slides on its axial direction or can move axially the joint of (plunging).Figure 14 and 15 shows the Rzeppa constant velocity universal joint (after this being called the BJ-type) as typical fixed constant velocity universal joint.This fixed constant velocity universal joint comprises: outer ring 1 as the socket parts, has six axially extended arc ball groove 1b that are formed among its spherical inside surface 1a; Inner ring 2 as inner joint part, has six axially extended arc ball groove 2b that are formed among its spherical outer surface 2a; Six balls 3 are as the moment of torsion transfer member between the ball groove 2b of ball groove 1b that is placed in outer ring 1 and inner ring 2; And the retainer 4 that keeps described ball 3.
The center P of ball groove 1b and 2b and Q respectively from the joint center O on arbitrary side of center O by axial dipole field same distance (PO=QO).That is, the center P of the ball groove 1b of outer ring 1 by distance P O from 1 the opening side skew of the center O of spherical inside surface 1a in the outer ring.The center Q of the ball groove 2b of inner ring 2 is from center O offset distance QO on the inner side surface of outer ring 1 of spherical outer surface 2a.The center of the internal surface 1a of outer ring 1 and the outer surface 2a of inner ring 2 and joint center O coupling.
A connected axle (not shown) is connected to outer ring 1, and another axle 5 is connected to inner ring 2.Therefore, inner ring 2 has and is used for the flexuose or the splined hole 2c that cooperate with axle 5 flexuose or splined section.When the axis shape of outer ring 1 and inner ring 2 (work angle of joint) at an angle, in plane, keep balls 3, thereby guarantee inner ring and outer ring constant angular speed by retainer 4 perpendicular to the bisector of work angle.
In the fixed constant velocity universal joint that uses eight balls, the optimization indoor design, identical with the fixed constant velocity universal joint that guarantees six balls of durability and intensity and use.See Japanese unexamined patent document H9-177814,2003-4062 and 2003-307235.
Summary of the invention
In fixed constant velocity universal joint, when transmitting moment of torsion on work angle, ball moves in retainer pocket hole (cage pocket) along the circumferencial direction and the radial direction of retainer.In the fixed constant velocity universal joint that uses six balls, when joint formed maximum work angle, the thickness of retainer satisfied moving radially of ball.In other words, as long as the ball point of contact falls into retainer pocket hole, minimum thickness just is set.This is because such fact: the increase of retainer thickness shoals the ball groove of outer ring and inner ring, has therefore reduced the fatigue life in high angle and high loading upper connection.
In the fixed constant velocity universal joint that can realize eight balls of use that size and weight further reduce, guarantee on high work angle intensity with identical at the fixed constant velocity universal joint that uses six balls be important.In order to improve the intensity of retainer, the thickness of retainer must increase.Yet when the thickness of retainer increased, the degree of depth of the ball groove of outer ring and inner ring shoaled.When the degree of depth of the ball groove of outer ring and inner ring shoaled, on high angle and high torque load, the contact ellipse of ball ran on the shoulder of ball groove, causes reducing of fatigue life.
In addition, in using the fixed constant velocity universal joint of eight balls, guarantee the fixed constant velocity universal joint of six balls of retainer intensity and use on high work angle identical be important.In using the fixed constant velocity universal joint of eight balls, the optimization by indoor design as described above guarantees that the fixed constant velocity universal joint of six balls of retainer intensity and use on high work angle is identical.However, described retainer thickness is thinner than the retainer thickness in the fixed constant velocity universal joint that uses six balls.
Main purpose of the present invention is retainer intensity and the fatigue life on high angle and high torque load that guarantees in the fixed constant velocity universal joint that uses eight balls on the high angle.
In order to guarantee the intensity of retainer on high angle in the fixed constant velocity universal joint that more stably transmits ball that uses eight moments of torsion, it is important that heat treatment becomes.Therefore, the present invention concentrates on the ratio that non-hardened layer occupies in the beam of retainer, and described ratio is as allowing retainer intensity reach maximum heat treatment procedure in the fixed constant velocity universal joint that uses eight moments of torsion transmission balls.
That is, when it was the BJ type, fixed constant velocity universal joint of the present invention had: the socket parts, and eight that have in the spherical inside surface that is formed at described socket parts extend axially arc ball groove; Inner joint part, eight that have in the spherical outer surface that is formed at described inner joint part extend axially arc ball groove; Eight balls, each of described eight balls are arranged between a pair of ball groove of socket parts and inner joint part, are used to transmit moment of torsion; And retainer, described retainer is arranged on and is used to keep described ball between socket parts and the inner joint part,
Each of the center of the center of the ball groove of socket parts and the ball groove of the inner joint part center of relative spherical inside surface and center of spherical outer surface respectively in axial direction is offset same distance (F) on opposite sides to each other,
The area of non-hardened layer is set to 0.30≤C/S≤0.75 to the ratio C/S of the cross-section area S of the beam of retainer.
When it was the UJ type, fixed constant velocity universal joint of the present invention had: eight of having in the spherical inside surface that is formed at described socket parts of socket parts, described socket parts extend axially arc ball groove; Inner joint part, eight that have in the spherical outer surface that is formed at described inner joint part extend axially arc ball groove; Eight balls, each of described eight balls are arranged between a pair of ball groove of socket parts and inner joint part, are used to transmit moment of torsion; And retainer, described retainer is arranged on and is used to keep described ball between socket parts and the inner joint part,
The center of the relative endosphere of each difference at the center of the center of the ball groove of described socket parts and the ball groove of described inner joint part and the center of ectosphere be the identical distance (F) of skew on opposite sides to each other in axial direction, the spherical inside surface of described retainer is offset identical distance (f) with the center of spherical outer surface along axial direction on opposite sides to each other, and be provided with on each ball groove of joint component and inner joint part outside and have the straight part of straight bottom, and
The area C of non-hardened layer is set to 0.30≤C/S≤0.75 to the ratio C/S of the cross-section area S of the beam of retainer.
According to the present invention, can obtain to have outstanding durability and stablize high-intensity retainer, thus the retainer intensity on high angle in the fixed constant velocity universal joint that can more stably guarantee to use eight moments of torsion to transmit ball.
When read in conjunction with the accompanying drawings, these and other objects of the present invention and feature will become more obvious from following description.
Description of drawings
Fig. 1 is the sectional view according to the retainer of embodiments of the invention;
Fig. 2 is the schematic section of the beam of retainer shown in Figure 1;
Fig. 3 is the longitdinal cross-section diagram of retainer shown in Figure 1;
Fig. 4 shows the ratio (C/S) that non-hardened layer occupies and the view of the relation between the retainer intensity in the beam of retainer;
Fig. 5 is the longitdinal cross-section diagram of fixed constant velocity universal joint;
Fig. 6 is the sectional view of joint shown in Figure 5;
Fig. 7 is the part zoomed-in view of Fig. 5;
Fig. 8 is the part zoomed-in view of Fig. 6;
Fig. 9 is the part zoomed-in view of Fig. 7;
Figure 10 is the longitdinal cross-section diagram according to the fixed constant velocity universal joint of another embodiment of the present invention;
Figure 11 is the longitdinal cross-section diagram of the joint on maximum work angle, shown in Fig. 5;
Figure 12 is the longitdinal cross-section diagram of retainer in the joint shown in Figure 11;
Figure 13 shows the view of the relation between the relative retainer thickness with admissible torque load of retainer intensity;
Figure 14 is the longitdinal cross-section diagram of existing fixed constant velocity universal joint;
Figure 15 is the sectional view of the joint shown in Figure 14.
Embodiment
At first, will describe according to BJ type in the embodiment shown in Fig. 5-7.As shown in FIG., fixed constant velocity universal joint comprises outer ring 10, inner ring 20, ball 30 and retainer 40.
Outer ring 10 as the socket parts is shapes of cup or clock, and comprises shaft portion 18 on its closure is distolateral, is used to be connected to one of connected two axles.Outer ring 10 has spherical interior perimeter surface, that is, the endosphere 12 that extends on the axial direction and eight arc ball grooves 14 are formed on circumferential direction in the endosphere 12 with regular spaces.
Have as the inner ring 20 of inner joint part and to be used for the zigzag fashion (serrated) or spline (splined) hole 28 that are connected with another one (being axle 5 herein) connected two axles.Inner ring 20 has spherical outer surface, that is, the ectosphere 22 of Yan Shening and eight arc ball grooves 24 are formed in the ectosphere 22 on the circumferential direction with regular spaces in the axial direction.
The ball groove 14 of outer ring 10 and the ball groove 24 of inner ring 20 form in pairs, are installed in ball groove 14 and the track of ball groove 24 as a pair of formation as the ball 30 of moment of torsion conveying element.Keep eight balls 30 altogether by retainer 40.Retainer 40 has interior perimeter surface of spherical outer surface or ectosphere 42 and sphere or endosphere 44 described ectospheres 42 and endosphere 44 and has identical central.Ectosphere 42 contacts with the endosphere 12 of outer ring 10, and endosphere 44 contacts with the ectosphere 22 of inner ring 20.
In this embodiment, ball groove 14 and 24 center P and Q are offset with same distance (PO=QO=F) by on arbitrary side of joint center O respectively in the axial direction.That is, by the center P (external orbital center) of distance P O from the ball groove 14 of the center O of endosphere 12 10 opening side skew outer ring 10 in the outer ring.The center Q of the ball groove 24 of inner ring 20 (inner tracks center) is from center O offset distance QO on the inner side surface of outer ring 10 of ectosphere 22.
The center of the ectosphere 42 of retainer 40 and overlap with the joint center O as the center of endosphere 12 of the outer ring 10 of the guiding surface of the ectosphere 42 that is used for retainer 40.The center of the endosphere 44 of retainer 40 and also overlap with the joint center O as the center of ectosphere 22 of the inner ring 20 of the guiding surface of the endosphere 44 that is used for retainer 40.Therefore, the skew of outer ring 10 (PO=F) equals the distance between the center P of ball groove 14 and the joint center O on the axial direction, and the skew of inner ring 20 (QO=F) equals the distance between the center Q of ball groove 24 and the joint center O in the axial direction, this means that (PO QO) equates.
The center P of the ball groove 14 of connection outer ring 10 and the center O of ball 30 3The length PO of line 3Equal to connect the center Q of ball groove 24 of inner ring 20 and the center O of ball 30 3The length QO of line 3In Fig. 5, represent this length by symbol PCR.In addition, as shown in Figure 7, suppose the center P of the ball groove 14 by connecting outer ring 10 and the center O of ball 30 3Line and the center O of jointing center O and ball 30 3The angle that limits of line be known as the outer race track offset angle o, and the center Q of the ball groove 24 by connecting inner ring 20 and the center O of ball 30 3Line and the center O of jointing center O and ball 30 3The angle that limits of line be known as the inner race track offset angle i, the outer race track offset angle oEqual the inner race track offset angle i
Use this structure, one of two axles that will be connected (coupled) are connected to outer ring 10, and another is connected to inner ring 20.When outer ring 10 and inner ring 20 formation work angles, the ball 30 that keeps by retainer 40 is maintained within the plane of the bisector (bisector) perpendicular to work angle.Therefore, the center O of ball 3And the center P of ball groove and the distance P O between the Q 3And QO 3(PO is equal to each other 3=QO 3=PCR), guarantee that the angular velocity of joint is constant.
As described above, just obtain permissible torque load, retainer intensity, durability and performance reliably, preferably establish the skew (F=PO=QO) of ball putting groove 14 and 24, ratio R 1=F/PCR falls into 0.069≤R like this 1In≤0.121 the scope.In this embodiment, R 1Be set to 0.104 (or 0.1038).R in the comparative product (fixed constant velocity universal joints of six balls of use shown in Figure 14 and 15) 1Common value be 0.14, R in this embodiment 1More less than the R of comparative product 1
Fig. 8 is the part zoomed-in view of Fig. 6, and shows the correlation of outer ring 10, inner ring 20 and ball 30.Each that is formed on ball groove 14 in the endosphere 12 of outer ring 10 has Gothic arch (Gothic arch) cross section, and each that is formed on ball groove 24 in the ectosphere 22 of inner ring 20 has Gothic arch (Gothic arch) cross section.Therefore, ball 30 is at two some C 11And C 12The place contacts with the ball groove 14 of outer ring 10, and at 2 C 21And C 22The place contacts with the ball groove 24 of inner ring 20.By center O by ball 30 3With point of contact C 11, C 12, C 21And C 22Line and the center O by ball 30 3The angle [alpha] that limits with the line of joint part O is known as wrapping angle.At point of contact C 11, C 12, C 21And C 22The wrapping angle α at place all equates, and is set to 29 ° to 40 °.29 ° to 40 ° wrapping angle α is less than undercutting universal joint (the undercut free joints of the routine of using six balls; UJ) and use 37 ° to 45 ° contact angle in the fixed constant velocity universal joint of six balls.By wrapping angle α is set is 29 degree or bigger, has limited the contact pressure between ball groove and the ball, and therefore can keep being equal to or higher than the durability in the conventional products.
Fig. 9 is the part zoomed-in view that is used to explain Fig. 7 that oppositely begins the angle of the angle of wedge (wedge angle).As described above, by the point of contact C between the ball groove 14 of ball 30 and outer ring 10 1Common normal line (common normal) H 1With by the point of contact C between the ball groove 24 of ball 30 and inner ring 20 2Common normal line H 2Angle be known as the angle of wedge 2 τ.Similarly, common normal line H 2Be to connect the point of contact between inner ring 20 and the ball 30 and the center O of ball 30 33 d-line.As shown in Figure 9, since the cause of arc ball groove 14, point of contact C between the ball groove 14 of outer ring 10 and the ball 30 1Pass through the center O of ball 30 relatively 3Joint median plane tilt angle tau.Since the cause of curved ball groove 24, the ball groove 24 of inner ring 20 and the point of contact C of ball 30 2Pass through the center O of ball 30 relatively 3Joint median plane tilt angle tau.The angle of wedge is corresponding to these angles τ sum, i.e. 2 τ.The stage of the angle of wedge 2 τ when the work angle of joint increases diminishes, and be reverse then.The angle of wedge 2 τ begin reverse work angle and are set to 9 ° or bigger.
Figure 10 shows the embodiment of UJ type.This embodiment is identical with the foregoing description shown in Figure 5, be respectively formed at except straight part 16 and 26 in the ball groove 24 of the ball groove 14 of outer ring 10 and inner ring 20, and the center p of the ectosphere 42 of the endosphere 44 of retainer 40 and q are offset identical apart from f on axial direction opposite each other.
Then, as shown in Figure 11, compare with the conventional fixed constant velocity universal joint that uses six balls, in using the fixed constant velocity universal joint of eight balls, explanation is used for guaranteeing on the high angle to equate or higher retainer intensity and guarantee the best retainer thickness of fatigue life on high angle and high loading.Figure 11 shows the state that the joint shown in Fig. 5 forms maximum work angle θ max.Appear at ball in the top of accompanying drawing with reference number 30a indication, ball 30a is in wherein said ball 30a and is positioned in the most radially inner stage of retainer.Appear at ball in the bottom of accompanying drawing with reference number 30b indication, ball 30b was in the stage that wherein said ball 30b is positioned in the radially outward location of retainer.Figure 12 is the longitdinal cross-section diagram of retainer 40, wherein by the two point chain line ball 30a and 30b is shown, and is restricted to the radial motion of ball in the pocket hole 46 of retainer 40 apart from B between the center of ball 30a and 30b.The thickness of retainer 40 is radial dimensions of the circumferentially extending wall in pocket hole 46, and by the symbol of the reference among Figure 12 AExpression.
The thickness of supposing retainer 40 is A, be used for joint rotate a circle, at maximum work angle θ MaxOn moving radially of ball 30 be B, the thickness of retainer 40 is set up, thereby satisfies the scope of 0.45≤B/A≤0.65 in the BJ type, and satisfies 0.65≤B/A in the UJ type≤0.85 scope.The scope that is used for the optimum value of UJ type with the different reason that is used for the BJ type is: as above described with reference to Figure 10, the ball groove 14 of outer ring and inner ring and 24 has straight part 16 and 26 respectively in the UJ type, and therefore compare with the BJ type, the ball groove shoals on the inboard of joint.
Figure 13 has described the meaning of above-mentioned number range.Although the numerical value among Figure 13 relates to the BJ type, in the UJ type, also can find similar trend.In the figure, based on the ball groove and the contact stress between the ball (Hertzian stress) of outer and inner circle, the T100 moment of torsion is the basic moment of torsion that is used to calculate the life-span of constant velocity universal joint, and refers to the moment of torsion that can obtain 1500 hours life-span on 100rpm.
As shown in Figure 13, in other words, under the situation of B/A＜0.45,, can guarantee the abundant intensity of retainer when retainer 40 thickness A during greater than the necessary thickness of radial motion B at the pocket hole of retainer 40 46 endospheres 30.But the degree of depth of the ball groove of outer ring and inner ring (on the inboard) becomes too shallow, thereby the contact ellipse of ball 30 is left the ball groove on maximum work angle, and has reduced torque load terrifically, causes the possible damage of function of butt joint.On the other hand, in other words, under the situation of B/A＞0.65, when the tolerance (allowance) of retainer thickness A relatively the ball 30 in the pocket hole 46 of retainer 40 radial motion B than hour, can guarantee the abundant degree of depth of the ball groove of outer ring and inner ring (on the inboard), thereby even make the contact ellipse of ball 30 on maximum work angle, also can not leave the ball groove.However, it is too thin that the thickness A of retainer 40 becomes, and can not guarantee the intensity at the high angle holder like this.In the UJ type of using eight balls, also can find the trend in the BJ type.Yet owing to the difference as above-mentioned structure, number range differs from one another.
As described above, the optimum thickness of retainer need be configured to satisfy the retainer intensity on high angle and the durability of high angle upper connection.Optimum thickness falls into above-mentioned scope (in BJ type 0.45≤B/A≤0.65,0.65≤B/A in the UJ type≤0.85).
Incidentally, the retainer of fixed constant velocity universal joint is made by the retainer hardened steel that is used for the machine construction purposes (hardening steel) usually, and described retainer will carry out carburizing and quenching.Retainer needs high strength (static strength and fatigue strength), to bear high moment of torsion and cyclic loading.In addition, because the contacting of metal and metal between the parts of fixed constant velocity universal joint needs wear resistance.For this reason, retainer need be heat-treated, and is used for fixing the necessary function of constant velocity universal joint thereby satisfy.Particularly in the fixed constant velocity universal joint that uses eight balls, compare with the fixed constant velocity universal joint that uses six balls, retainer is thinner, and the cross-section area of the beam between the pocket hole 46 (bar) 48 is littler.Therefore, retainer intensity is tending towards being subjected to the bigger influence of heat treatment procedure.
Therefore, using eight moments of torsion to transmit in the fixed constant velocity universal joint of balls, the ratio that non-hardened layer occupies in the beam 48 of retainer 40 is known as allowing the intensity of retainer 40 reach maximum heat treatment procedure.Herein, as decorating shown in (pearskin finish) by the pears epidermis among Fig. 2, non-hardened layer refers to the core part of Vickers (Vickers) hardness number that has less than Hv513.As shown in Figures 1 to 3, the cross-section area of supposing the beam 48 between the pocket hole 46 of retainer 40 is S, and the area of the non-hardened layer of beam 48 is C, and the ratio C/S of the area C of non-hardened layer and the cross-section area S of beam 48 is set up the scope that falls into 0.30≤C/S≤0.75.
Satisfy above-mentioned scope when the carbon depth of penetration of retainer 40 is set up, can realize the maximum strength of retainer 40.When C/S less than lower limit 0.30, the core of beam 48 (non-hardened layer part) becomes too little, and retainer 40 lost the toughness of described retainer 40, causes intensity to reduce.On the other hand, though when the upper limit of C/S greater than 0.75 the time, also satisfy intensity, still, consider fatigue life (wearing and tearing), the upper limit need be set to 0.75 or littler.
Fig. 4 shows the result of the strength test of the sample execution of having used the carbon depth of penetration that has retainer 40 in the fixed constant velocity universal joint that uses eight moments of torsion transmission balls.In Fig. 4, horizontal axis is represented C/S, and vertical shaft is represented retainer intensity.From this figure, clearly, be that optimum value can make retainer intensity reach maximum by C/S is set.

Claims (6)

1. fixed constant velocity universal joint comprises: the socket parts, and eight that have in the spherical inside surface that is formed at described socket parts extend axially arc ball groove; Inner joint part, eight that have in the spherical outer surface that is formed at described inner joint part extend axially arc ball groove; Eight balls, described eight balls are arranged between the ball groove of socket parts and inner joint part, are used to transmit moment of torsion; And retainer, described retainer is arranged on and is used to keep described ball between socket parts and the inner joint part, wherein
The edge, center of relative respectively described interior spherical surface of each of the center of the ball groove of described socket parts and described inner joint part and described outer spherical surface in axial direction is offset same distance (F) on opposite sides to each other, and
The area of non-hardened layer is set to 0.30≤C/S≤0.75 to the ratio C/S of the cross-section area S of the beam of retainer.
2. fixed constant velocity universal joint comprises: the socket parts, and eight that have in the spherical inside surface that is formed at described socket parts extend axially arc ball groove; Inner joint part, eight that have in the spherical outer surface that is formed at described inner joint part extend axially arc ball groove; Eight balls, described eight balls are arranged between the ball groove of socket parts and inner joint part, are used to transmit moment of torsion; And retainer, described retainer is arranged on and is used to keep described ball between socket parts and the inner joint part, wherein
The center on relative respectively described interior spherical surface of each of the center of the center of the ball groove of described socket parts and the ball groove of described inner joint part and the described surface of described ectosphere in axial direction is offset same distance (F) on opposite sides to each other, the center on the outer and inner ball surface of retainer is offset identical distance (f) along axial direction on opposite sides to each other, and setting has the straight part of straight bottom on each ball groove of described socket parts and described inner joint part, and
The area C of non-hardened layer is set to 0.30≤C/S≤0.75 to the ratio C/S of the cross-section area S of the beam of retainer.
3. according to the described fixed constant velocity universal joint of claim 1, the thickness of wherein supposing retainer is A, and the radial motion of maximum the above ball of work angle is B, satisfies the relation of 0.45≤B/A≤0.65.
4. according to the described fixed constant velocity universal joint of claim 2, the thickness of wherein supposing retainer is A, and the radial motion of maximum the above ball of work angle is B, satisfies the relation of 0.45≤B/A≤0.65.
5. according to the described fixed constant velocity universal joint of claim 1, the surface hardness scope of wherein said retainer is between HRC58 and HRC63, and the core hardness scope is between HRC25 and HRC45.
6. according to the described fixed constant velocity universal joint of claim 2, the surface hardness scope of wherein said retainer is between HRC58 and HRC63, and the core hardness scope is between HRC25 and HRC45.
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Cited By (2)

* Cited by examiner, † Cited by third party
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Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1097567A (en) * 1911-01-21 1914-05-19 Busch Sulzer Bros Diesel Engine Co Combustion-engine.
CA2016894A1 (en) * 1989-07-25 1991-01-25 Werner Krude Constant velocity universal joint
WO1997024538A1 (en) * 1995-12-26 1997-07-10 Ntn Corporation Constant velocity universal coupling
JP3702019B2 (en) 1995-12-26 2005-10-05 Ｎｔｎ株式会社 Fixed constant velocity joint
JP2003307235A (en) 1996-05-28 2003-10-31 Ntn Corp Constant velocity universal joint
JP3767168B2 (en) 1998-04-30 2006-04-19 日本精工株式会社 Constant velocity joints and rolling bearing units for wheels with constant velocity joints
US6299542B1 (en) * 1998-04-15 2001-10-09 Nsk Ltd. Constant velocity joint and rolling bearing unit for wheel
JP3909992B2 (en) * 1999-11-30 2007-04-25 Ｎｔｎ株式会社 Cage of fixed type constant velocity universal joint, manufacturing method thereof, and fixed type constant velocity universal joint
US6506122B2 (en) * 2000-05-19 2003-01-14 Ntn Corporation Constant velocity universal joint
JP2002188653A (en) * 2000-12-20 2002-07-05 Ntn Corp Uniform motion universal joint
JP2003004062A (en) 2001-06-25 2003-01-08 Ntn Corp Stationary type constant velocity universal coupling
US20030017877A1 (en) * 2001-04-24 2003-01-23 Masazumi Kobayashi Constant velocity universal joint
JP4133415B2 (en) * 2003-02-18 2008-08-13 Ｎｔｎ株式会社 Fixed type constant velocity universal joint
JP4223358B2 (en) * 2003-09-04 2009-02-12 Ｎｔｎ株式会社 Fixed constant velocity universal joint

Cited By (3)

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JP2006258170A (en) 2006-09-28

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